Beverage dispensing apparatus

ABSTRACT

A beverage dispensing device for dispensing pressurized beverages at a high flow rate without producing excessive foaming comprising a streamlined valve assembly and a downward extending nozzle assembly which permits a range of containers to be filled from the bottom.

[0001] The present invention relates to an apparatus for dispensingcarbonated or pressurized beverages, and more specifically to anapparatus for dispensing carbonated or pressurized beverages at highflow rates with minimal foaming.

BACKGROUND OF THE INVENTION

[0002] Pressurized beverages, such as beer, are produced in a mannerthat the beverage contains a certain amount of dissolved gas, typicallycarbon dioxide (CO₂). While a certain amount of dissolved CO₂ occursnaturally in the beer brewing and fermentation process, most largecommercial breweries dissolve additional CO₂ into their product. Addingadditional CO₂ serves two main purposes for the commercial breweries.First, from a quality control standpoint, all the beer produced can bemodified to contain the same amount of CO₂. Second, the additional CO₂gives the beer a more effervescent quality, which is perceived by theconsumer as having better crispness and flavor.

[0003] Beer produced by most major breweries contains between 10 and 15psi (68950 and 103425 Newtons per square meter) of dissolved CO₂. Sinceatmospheric levels of CO₂ are substantially smaller, beer has a tendencyto release some of its dissolved CO₂ when exposed to the ambientatmosphere. Due to the complex chemical makeup of beer, foam tends toform when this dissolved CO₂ comes out of solution.

[0004] Additional parameters contributing to the amount of foamoccurring in beer include temperature and turbulence. The physicalproperties of liquids dictate that the higher the liquid temperature,the lower its capacity for dissolved gasses. Thus, the greater thetemperature of beer, the greater the tendency for its dissolved gassesto come out of solution and the greater the tendency of the beer tofoam. Turbulence and other forms of agitation produce regions of sudden,extreme pressure variation within the beer that cause CO₂ to come out ofsolution in the form of foam.

[0005] While much of the beer produced by the major commercial breweriestends to be packaged in bottles and cans, a large volume of beer is alsopackaged in large, sealed containers known as kegs. Kegs are reusableand refillable aluminum containers that allow for efficient, sanitaryhandling, storage and dispensing of typically 15.5 gallons (58.7 liters)of beer. Beer packaged into kegs, called keg beer, is commonly served atbars, taverns, night clubs, stadiums, festivals and large parties.

[0006] Dispensing keg beer into open containers for consumption requiresspecialized equipment. The beer dispensing faucet (commonly called thebeer tap) comprises a valve and a spout for controlling and directingthe flow of beer into an open container. Beer often foams as it isdispensed from conventional faucets. One cause of such foaming is simplythe pressure differential between CO₂ dissolved in the beer and CO₂present in the ambient atmosphere; CO₂ will naturally be released fromthe beer when the beer is exposed to the atmosphere. Another cause ofsuch foaming is the turbulent nature by which beer is dispensed fromconventional faucets; even when dispensed carefully, beer splashes ontothe walls and bottom of the container and foam results.

[0007] A small amount of foam is often desirable. Beer that has not beenstored properly often loses its dissolved CO₂ to the atmosphere and isconsidered to be flat. Thus, a small amount of foam indicates to theconsumer that the beer is fresh. Additionally, beer marketers have beensuccessful in portraying the perfect container of beer as possessing afrothy layer of foam. On the other hand, too much foam is undesirable tothe consumer and the beverage vendor. Since foam fills up a containerwith CO₂ instead of with liquid beer, excessive amounts of foam leavethe consumer dissatisfied, often to the point of requesting a newcontainer be served. Knowing this, vendors are left with two choices.They can partially fill a container, wait for the foam to dissipate andthen add additional beer, a time-consuming process. Alternatively, theycan pour out excess foam as they are filling the container, wasting beerin the process.

[0008] Since excessive foaming is problematic for both the consumer andthe vendor, attempts have been made to design beer dispensing systemsthat are installed and configured in a manner that ideally achievesoptimal amounts of foam in the dispensing process. In addition tomaintaining the beer at a constant, cold temperature throughout thedispensing process, conventional beer dispensing systems are configuredto pour beer at a slow enough flow rate that beer exits the faucet at avelocity that does not cause foaming when the beer impacts thecontainer.

[0009] Conventional systems are optimized for a flow rate of one U.S.gallon (3.785 liters) per minute. While such a flow rate is suitable formost low-volume dispensing applications, there are many situations inwhich it would be beneficial for both the vendor and the consumer ifbeer could be dispensed more quickly while still maintaining optimalamounts of foam. At busy bars, taverns, festivals, large parties andstadiums, consumers often must wait in long lines before being served.Under these circumstances, it would be desirable for both the vendor andthe consumer for beer to be dispensed more quickly.

[0010] Previous beer dispensing systems have been designed to dispensebeer more quickly than the standard one U.S. gallon per minute flowrate. One drawback with these systems is that they typically employelaborate electronic control mechanisms, making them expensive tomanufacture and maintain. Additionally, some of these systems employ theuse of a reservoir near the point of the faucet making the devices largeand difficult to clean. Moreover, the retrofit of such devices ontoexisting bar tops can be difficult and expensive.

SUMMARY OF THE INVENTION

[0011] The present invention is directed to a beverage dispensing devicefor dispensing pressurized beverages at a flow rate substantially higherthan prior mechanical tap apparatus without producing excessive foaming.It can be implemented as a purely mechanical device so as to keepmanufacturing and maintenance costs low. In addition, the presentinvention can be implemented without the use of reservoirs at or nearthe point of dispensing, thus facilitating cleaning and retrofitting toexisting bar tops.

[0012] In a preferred embodiment, the present invention comprises abeverage dispensing apparatus for dispensing a pressurized beveragecomprising a nozzle through which the pressurized beverage at leastinitially exits at atmospheric conditions having an internal passageway,a liquid receiving end adapted to attach as the end element of apressurized beverage dispensing system, and a liquid dispensing end thatdispenses the pressurized beverage at least initially to atmosphericconditions, wherein the cross-sectional area of the internal passagewayof the nozzle decreases from the liquid receiving end to the liquiddispensing end.

[0013] In another embodiment, the present invention comprises an upwardextending neck, a streamlined valve assembly and a downward extendingnozzle assembly. The overall shape and size of the device permits arange of containers to be filled from the bottom. Additionally, thenozzle assembly contains a streamlined flow redirecting component thatserves to generally radially disperse liquid flow. Thus, the amount offoaming that occurs when beer is dispensed at fast rates is desirablyreduced.

[0014] In one embodiment, the horizontal cross-sectional area of thenozzle gradually decreases from the top of the nozzle to the bottom orliquid dispensing end of the nozzle. Preferably, the profile of thisdecreasing cross-sectional area is consistent with that of a liquidstream falling under the force of gravity in the absence of such anozzle. A nozzle with this shape ensures that liquid flowing through itremains in substantially continuous contact with the interior wall ofthe nozzle. In this way, air from the liquid dispensing end of thenozzle is prevented from bubbling up into the nozzle. Additionally, theviscous forces acting between the nozzle interior wall and the liquidflowing through the nozzle serve to counteract the accelerationexperienced by the liquid in the nozzle due to gravitational forces.

[0015] In another embodiment of the invention, flow-straighteningelements are added to the nozzle which serve to make the flow of liquidthrough the nozzle less turbulent. Such elements also increase theamount of surface area across which decelerating viscous forces can takeeffect.

[0016] In another embodiment of the invention, the device is able toselectively dispense beer at two different flow rates. In such anembodiment a pressure-reducing element is integrated into the devicealong with a multi-way valve that selectively routes liquid through thepressure-reducing element. When the valve is positioned such that liquidfirst flows through the pressure reducer before entering the rapidbeverage dispensing device, liquid is dispensed at a reduced rate,preferably the optimal rate of conventional beer dispensing faucets.When the valve is positioned such that liquid bypasses the pressurereducer, the rapid beverage dispensing device functions at its fasterflow rate.

[0017] Because the rapid beverage dispensing device is capable ofdispensing beer at at least twice the flow rate of conventional beerdispensing systems while still achieving optimal levels of foam, it alsotends to attract attention from beverage consumers as an object ofcuriosity. This attraction can be heightened by forming components ofthe device from transparent material to allow consumers to see thebeverage flowing therein.

[0018] Further advantages and features of the embodiments of the presentinvention will be apparent from the following detailed description ofthe invention in conjunction with the associated drawings.

BRIEF DESCRIPTION OF THE DRAWINGS

[0019]FIG. 1 is a side elevation view showing the components of abeverage dispensing system with a schematic sectional view of the firstembodiment of the rapid beverage dispensing device.

[0020]FIG. 2 is a close-up schematic sectional view of the rapidbeverage dispensing device of FIG. 1.

[0021]FIG. 3 is a schematic perspective view of a second embodiment ofthe rapid beverage dispensing device where the neck assembly is replacedby a tall draft dispensing tower.

[0022]FIG. 4 is a close-up schematic sectional view of the valveassembly of FIG. 2 with the valve shown in the closed position.

[0023]FIG. 5 is a side elevation view of another embodiment of astreamlined valve member for use in the valve assembly of FIG. 2.

[0024]FIG. 6 shows a side elevation view of yet another embodiment of astreamlined valve member for use in the valve assembly of FIG. 2.

[0025]FIG. 7 is a sectional schematic view of the valve assembly of FIG.4 with the valve shown in the open position.

[0026]FIG. 8 is a perspective view of the streamlined valve member ofFIG. 4 illustrating the curvature and overall shape of the liquid-facingsurface of the valve shoulder.

[0027]FIG. 9 is a cross sectional perspective view of the valve neck andvalve shoulder.

[0028]FIG. 10 is a schematic sectional view of a conventional beerdispensing faucet.

[0029]FIG. 11 is an illustration of the gravitational effects on liquidflowing from a conventional faucet.

[0030]FIG. 12 shows a schematic sectional view of another embodiment ofthe nozzle assembly where the parabolic profile of the nozzle crosssectional area of FIG. 2 is approximated by nozzle with a linear taper.

[0031]FIG. 13 shows a schematic sectional view of another embodiment ofthe nozzle assembly where the parabolic profile of the nozzle crosssectional area of FIG. 2 is approximated by a cylindrical nozzle.

[0032]FIG. 14 is a perspective sectional view of yet another embodimentof the nozzle assembly where the nozzle contains four semicircularflow-straightening channels.

[0033]FIG. 15 is a sectional view of a nozzle assembly containing twosemicircular flow-straightening channels.

[0034]FIG. 16 is a sectional view of a nozzle assembly containing sixsemicircular flow-straightening channels.

[0035]FIG. 17 is a sectional view of a nozzle assembly containing sevencircular flow-straightening channels.

[0036]FIG. 18 is a close-up, sectional schematic view of the nozzleassembly of FIG. 2 with a container present and liquid flow linesindicating the manner in which the flow redirector redirects liquidflow.

[0037]FIG. 19 is a perspective view of the flow redirector of FIG. 2.

[0038]FIG. 20 is sectional view of another embodiment of the flowredirector for use in the nozzle assembly of FIG. 2.

[0039]FIG. 21 is a sectional view of still another embodiment of theflow redirector for use in the nozzle assembly of FIG. 2.

[0040]FIG. 22 is a sectional view of yet another embodiment of the flowredirector for use in the nozzle assembly of FIG. 2.

[0041]FIG. 23 is a schematic sectional view of a nozzle assembly with aflow redirector whose position can be longitudinally adjusted.

[0042]FIG. 24 is a schematic sectional view of the nozzle assembly ofFIG. 23 with the flow redirector shown moved to a new position.

[0043]FIG. 25 is a schematic sectional view of the rapid beveragedispensing device containing a conical diffuser within its neckassembly.

[0044]FIG. 26 is a schematic sectional view of the rapid beveragedispensing device shown with a multi-way valve and a pressure reducingelement.

[0045]FIG. 27 is a close-up, schematic sectional view of the multi-wayvalve of FIG. 26 shown with the valve routing liquid in a manner thatbypasses the pressure-reducing element.

[0046]FIG. 28 is a close-up, schematic sectional view of the multi-wayvalve of FIG. 26 shown with the valve routing liquid through thepressure-reducing element prior to directing liquid to the rapidbeverage dispensing device.

DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS OF THE INVENTION

[0047] As shown in FIG. 1, the rapid beverage dispensing device 35comprises a neck assembly 36, a valve assembly 37, and adownward-extending nozzle assembly 38. In a preferred embodiment, neckassembly 36 is substantially vertical. The rapid beverage dispensingdevice 35 is designed to attach to a conventional pressurized beveragedispensing system, such as a beer dispensing system 39 that includes abeer keg 40 or similar beverage-containing reservoir and beverage tubing41 for conveying a beverage from a container or beer keg 40 to the rapidbeverage dispensing device 35. A shank 42 connects the rapid beveragedispensing device 35 to beverage tubing 41. Keg tapping device 43connects beverage tubing 41 to beer keg 40. Draft dispensing tower 44supports shank 42.

[0048] Beer produced by most major manufacturers in the United States isformulated to be stored and served optimally at approximately 38 degreesFahrenheit (3.3 degrees Celsius). If the beer is warmer than thisoptimal temperature, it will tend to release too much carbon dioxide(CO₂) when it is dispensed. If the beer is colder than this optimaltemperature, it will tend to retain too much CO₂ when it is dispensedand have a muted flavor. Since most systems are not able to maintain aprecise temperature, a range between 36 and 40 degrees Fahrenheit (2.2and 4.4 degrees Celsius) is generally considered acceptable.Accordingly, in one embodiment, the beer dispensing system 39 of thepresent invention has the ability to cool various elements of the systemand maintain these elements within this acceptable temperature range.

[0049] As shown in FIG. 1, in many dispensing systems beer in thebeverage tubing 41 is kept cold by circulating a cold liquid throughcoolant tubing 45 bundled with beverage tubing 41. Such systemstypically involve refrigerating and circulating glycol through means ofa glycol refrigeration device 46 and a glycol pump 47. Alternatively,some systems blow cold air through conduits containing the beveragetubing 41 as a means of keeping the beverage tubing 41 cold.

[0050] Beer contained in a beer keg 40 requires an energy source forconveying the beverage from the beer keg 40 through the entire beerdispensing system 39 to the rapid beverage dispensing device 35. Suchenergy is commonly provided via pressurized gas, typically pressurizedCO₂. As shown in FIG. 1 in these systems, a tank 48 containingpressurized CO₂ is connected to beer keg 40 via a pressurized gas hose49. Pressure regulating device 50 serves as a means to adjust thepressure of the CO₂ driving the beer through the beer dispensing system39. In systems where a large distance exists between the beer keg 40 andthe rapid beverage dispensing device 35, a second gas may be used toprovide added pressure for moving the beer through the beverage tubing41. Pressurized nitrogen (N₂) housed in nitrogen tank 51 may be used asthis second gas. Nitrogen tank 51 is connected to beer keg 40 via aseparate pressurized gas hose 49. A separate pressure regulating device50 serves as a means to adjust the additional pressure provided by thecompressed nitrogen. Some systems are able to extract nitrogen from theair, precluding the need for a separate nitrogen tank. Optionally, inanother embodiment, a system may use a mechanical pump (not shown) toprovide the energy required to move beer through the system in lieu of,or in addition to, pressurized gas.

[0051] The Reynolds number is a dimensionless parameter often used influid flow analysis. Fluid moving through round piping or tubingpossessing a Reynolds number under 2100 is said to exhibit laminar flow.A system with a Reynolds number greater than 4000 is said to exhibitturbulent flow. A system that is neither laminar nor turbulent is saidto exhibit transitional flow characteristics. The Reynolds number can becalculated using the following equation:${Re} = \frac{\rho \quad {VD}}{\mu}$

[0052] where

[0053] Re=Reynolds number

[0054] ρ=density of the liquid

[0055] V=linear velocity of the liquid

[0056] D=diameter of the tubing

[0057] μ=viscosity of the liquid

[0058] The pressure drop experienced by liquid moving through the rapidbeverage dispensing device 35 is one of several parameters thatdetermine the flow rate at which beer moves through the beer dispensingsystem 39. The flow rate is also influenced by the length, diameter androughness of the beverage tubing 41, the height differential between thebeer keg 40 and the rapid beverage dispensing device 35, and the energyprovided by the pressurized CO₂ and/or N₂. In particular, for fullydeveloped laminar liquid flow, the flow rate can be determined accordingto the following equation:$Q = \frac{\pi \quad D^{4}\Delta \quad p}{128\quad \mu \quad l}$

[0059] where

[0060] Q=volumetric flow rate

[0061] D is the diameter of the beverage tubing 41

[0062] Δp=the pressure differential between the beer keg 40 and therapid beverage dispensing device 35

[0063] μ=the viscosity of the beer or other liquid being dispensed

[0064] l=the length of beverage tubing 41 through which the beer flows

[0065] While the target flow rate for conventional beer dispensingfaucets is one U.S. gallon (3.785 liters) per minute, the rapid beveragedispensing device 35 has a target flow rate of at least twice that rate.Regardless of whether beer is flowing at one gallon per minute or threegallons per minute, for beverage tubing 41 possessing an inside diameterof under 1 inch, flow through the beverage tubing 41 is rarelycompletely laminar. Under these circumstances, the following equationapplies: $h_{L} = {f\quad \frac{l}{D}\frac{V^{2}}{2g}}$

[0066] where

[0067] h_(L)=head loss between sections 1 and 2 of the system

[0068] f=friction factor (function of beverage tubing 41 roughness andReynolds number)

[0069] l=length of beverage tubing 41

[0070] D=diameter of beverage tubing 41

[0071] V=linear velocity of the fluid

[0072] g=gravitational constant

[0073] Accordingly, as the beverage tubing 41 connecting the beer keg 40to the rapid beverage dispensing device 35 is lengthened and thediameter of the beverage tubing 41 is decreased, the amount of energyrequired from the pressurized CO₂ and/or N₂ must increase in order toovercome the additional pressure head loss. Additionally, the amount ofenergy required from the pressurized CO₂ must increase in order toincrease the velocity of the liquid moving through the beverage tubing41. Preferably, the beer dispensing system 39 is configured to deliverbeer at an increased flow rate to the point of the shank 42 permittingthe rapid beverage dispensing device 35 to provide increased pouringcapacity compared with conventional systems.

[0074] Neck assembly 36 of the rapid beverage dispensing device 35positions and supports the rapid beverage dispensing device 35 in amanner that allows for the bottom filling of a wide variety of containersizes, ranging from glasses to pitchers. To accommodate the bottomfilling of such containers, the distance between the distal end 52 ofnozzle assembly 38 and the top of a bar 53 or other structure directlybeneath it is preferably at least as great as the height of the largestcontainer to be filled. Preferably, there should be substantialclearance to allow a pitcher 54 to be placed directly beneath the nozzleassembly 38.

[0075] One embodiment of the rapid beverage dispensing device 35 of thepresent invention is shown in more detail in FIG. 2. In the embodimentshown in FIG. 2, the lower end 55 of the neck assembly 36 has threads 56to attach to a standard beer faucet shank 42 using a standard shankcoupling nut 57, compression ring 58 and compression washer 59, althoughother methods of attachment, including but not limited to flanges withO-rings and quick-disconnect fittings are contemplated. Additionally,neck assembly 36 may be permanently attached to shank 42 by welding orother means. In a common bar-top installation, shank 42 is attached to adraft dispensing tower column 60. A coupling gasket 61 is positionedbetween the shank 42 and the neck assembly 36 to ensure a tight seal.Within neck assembly 36 is a length of neck tubing 62 for conveyingliquid from the shank bore 63 to the valve assembly 37. The diameter ofthe neck tubing 62 preferably matches the diameter of the shank bore 63at the point of attachment between neck assembly 36 and shank 42.Preferably, neck tubing 62 at the lower end 55 of the neck assembly 36is initially aligned axially with the shank bore 63. In this embodiment,neck tubing 62 has about a 90 degree bend before continuing verticallywithin neck assembly 36. Neck tubing 62 then bends through an arc 64 ofabout 90 degrees near the upper end 65 of the neck assembly 36.Turbulence associated with a change in direction of liquid flow isreduced as the radius of the arc 64 increases. While an arc 64 with alarge radius would decrease the turbulence associated with changing thedirection of liquid flow, it would also result in the rapid beveragedispensing device 35 having a large horizontal distance between thedraft dispensing tower 44 and the nozzle assembly 38. Accordingly, theradius of arc 64 is preferably small enough for the nozzle assembly 38to be positioned directly over the bar-top drain 66. In a preferredembodiment, valve assembly 37 is attached to the upper end 65 of theneck assembly 36 such that liquid is able to move through the necktubing 62 and into the valve assembly 37 without leakage. Additionally,neck tubing 62 in the upper end 65 of the neck assembly 36 may increasein inside diameter as it approaches the valve assembly 37 such that theinside diameter of the neck tubing 62 matches the inside diameter of thevalve housing 94 at the point where the neck assembly 36 and the valveassembly 37 are joined.

[0076] Because neck assembly 36 is exposed to the ambient environment,beer residing in the neck tubing 62 during period of system inactivitycan become undesirably warm. To maintain beer in the neck tubing 62 atan appropriate serving temperature, neck assembly 36 may be filled withinsulation 67. In lieu of, or in addition to insulation 67, the neckassembly 36 may be cooled with glycol by extending coolant tubing 45into neck assembly 36 (not shown).

[0077] As shown in FIG. 3, in another embodiment of this invention, theneck assembly 36 of the rapid beverage dispensing device 35 is replacedwith a tall draft dispensing tower assembly 68 consisting of a talldraft dispensing tower column 69, a draft dispensing tower cover 70, adraft dispensing tower base 71, mounting screws 72, a shank 42, andcolumn insulation 73. In this embodiment, the valve assembly 37 attachesto a shank 42 affixed to the tall draft dispensing tower column 69.Valve assembly 37 may be attached to shank 42 using shank coupling nut57, compression ring 58, compression washer 59, and coupling gasket 61,although other means, including flanges with O-rings andquick-disconnect fittings, are contemplated. The distance between thebar top 53 and the shank 42 is such that the distance between the distalend 52 of the nozzle assembly 38 and the bar top 53 is greater than theheight of a standard pitcher 54. In this embodiment, no neck assembly isexposed to the ambient atmosphere and beer maintained at pressureupstream from the valve assembly 37 remains insulated from the ambientatmosphere within the tall draft dispensing tower assembly 68.Additionally, in this embodiment, the diameter of the shank bore 63 maygradually increase along its length such that, at one end, the diameterof the shank bore 63 is equal to the diameter of the beverage tubing 41,and that the diameter of the shank bore 63 matches the inside diameterof the valve housing 94 at the point where the valve assembly 37attaches to the shank 42.

[0078] In one embodiment, shown in FIG. 4, valve assembly 37 comprisesvalve member 74, handle lever 75, friction ring 76, bonnet washer 77,compression bonnet 78, valve chamber 79, valve seat 80, valve shoulderguide 81, exterior air vent hole 82 and interior air vent hole 83. Valvemember 74 may comprise valve head 84, valve neck 85, valve shoulder 86,and seat washer 87. Valve neck 85 may be affixed to valve head 84 by anymeans known. Preferably, valve neck 85 is affixed to valve head 84 by athreaded means such that the two parts can be dissembled. Seat washer 87may be held in place between valve head 84 and valve neck 85. Theoverall shape of the assembled valve head 84, seat washer 87 and valveneck 85 is streamlined so as to minimally disturb the liquid flowingaround it. Accordingly, the liquid-facing outer surface 88 of seatwasher 87 is contoured to blend smoothly, preferably tangentially, withthe outer surface 89 of the valve head 84. Additionally, theliquid-facing outer surface 88 of the seat washer 87 is contoured toblend smoothly, preferably tangentially with valve neck 85.

[0079] Other embodiments of valve member 74 are shown in FIG. 5 and FIG.6. In these embodiments, valve head 84 is generally spherical orelliptical in nature, the outer surface 88 of seat washer 87 iscontoured to generally blend smoothly with the outer surface 89 of thevalve head 84. Also, the outer surface 88 of seat washer 87 is contouredto generally blend smoothly into the valve neck 85. As shown in FIG. 4,valve shoulder 86 may be sized to slide longitudinally into the valveshoulder guide 81 with a tight circumferential tolerance so as to keepthe entire valve member 74 aligned axially with respect to the valvechamber 79. The distal end 90 of handle lever 75 fits into the valveshoulder slot 91. A ball joint 92 built into the handle lever 75 nestsin the ball seat 93 that is part of the valve housing 94. A frictionring 76 and bonnet washer 77 fit circumferentially around the top ofball joint 92. A compression bonnet 78 may also fit circumferentiallyaround the handle lever 75 and is held in place via threads in thecompression bonnet 78 and threads built into the valve housing 94. Whenthreaded into place, compression bonnet 78 pushes against the frictionring 76 and the bonnet washer 77 forming a seal that prevents beer fromleaking out of the valve assembly 37 through the ball seat 93.

[0080]FIG. 4 illustrates the valve assembly 37 with the valve member 74in the closed position. In this position, the proximal, threaded end 95of handle lever 75 may be angled toward valve head 84. Since handlelever 75 pivots about its ball joint 92, in this valve-closed position,the distal end 90 of the handle lever 75 is angled away from the valvehead 84, pulling the valve member 74 longitudinally until the seatwasher 87 comes into contact with the valve seat 80, forming a seal thatcuts off the flow of liquid. In this position, liquid in the valvechamber 79 and throughout the system will likely be at a pressuregreater than the ambient atmospheric pressure to prevent CO₂ from comingout of solution while the system is not pouring beer. Accordingly,pressure from the liquid in the valve chamber 79 combined with thefrictional forces acting between the valve shoulder 86 and the valveshoulder guide 81 and among the valve shoulder slot 91, the frictionring 76, the bonnet washer 77, the compression bonnet 78 and the handlelever 75 are sufficient to hold the valve member 74 in its closedposition. Consequently, despite the pressure of the liquid upstream ofthe valve member 74, no springs, locks, actuators or other componentsapplying an active force to the valve member 74 are required to maintainthe valve member 74 in its closed position. Additionally, with the valvemember 74 in the closed position, the valve shoulder slot 91 completes achannel between the exterior air vent hole 82 and the interior air venthole 83 allowing air to enter the upper part of the nozzle 99 tofacilitate more rapid and complete draining of any liquid in the nozzleassembly 38 the moment the valve member 74 is moved into the closedposition.

[0081] To open the valve member 74, the threaded end 95 of the handlelever 75 is moved forward, in a direction generally away from the valveseat 80. As the handle lever 75 is moved in this manner, it pivotswithin the ball seat 93 about the center of its ball joint 92 causingthe distal end 90 of the handle lever 75 to rotate in an oppositedirection. This movement of the distal end 90 of the handle lever 75serves to slide the valve member 74 in a direction that moves the seatwasher 87 away from the valve seat 80, thereby placing the valve member74 in the open position. Forces acting on the valve head 84 from theliquid flowing around it combined with frictional forces acting betweenthe valve shoulder 86 and the valve shoulder guide 81 and among thevalve shoulder slot 91, the friction ring 76, the bonnet washer 77, thecompression bonnet 78 and the handle lever 75 are sufficient to hold thevalve member 74 in its open position without the need to apply acontinuous active force to the handle lever 75 or valve member 74.

[0082] Preferably, disturbances to liquid flow are minimized by a valveassembly 37 which is as streamlined as possible. As illustrated by theliquid flow lines 96 in FIG. 7, liquid flowing through the valveassembly 37 is guided in an arcing manner into the nozzle assembly 38which is oriented in a generally downward direction. Accordingly, thevalve assembly 37 must not only serve to start and stop the flow ofliquid, but also to guide the liquid into the nozzle 99 while causing aslittle liquid flow disturbance as possible. As shown in FIG. 8, tofacilitate a smooth redirection of liquid flow, the liquid-facingsurface 97 of the valve shoulder 86 is contoured to match the curvatureof the interior surface of the valve housing 94 when the valve member 74is in its open position. In particular, in the embodiment shown here,the interior surface of the valve housing 94 near the valve shoulder 86is generally the shape of a portion of an arced cylinder. That is, theliquid-facing surface 97 of the valve shoulder 86 is generally concavein shape and posses two radii of curvature. The first radius matches thelarge radius of the arc formed by the valve housing 94 that guides theliquid into the nozzle 99. The second radius of curvature isperpendicular to the first and matches the inside radius of the valvehousing 94 at the point where the valve assembly 37 and the nozzle 99are joined. Alternatively, the liquid-facing surface 97 of the valveshoulder 86 may possess only the first radius of curvature, in whichcase the liquid-facing surface 97 of the valve shoulder 86 will stilldirect liquid flow in a streamlined manner into the nozzle 99.Additionally, the liquid-facing surface 97 of the valve shoulder 86 mayalso be planar, in which case the edges of such a plane should be flushwith the interior surface of the valve housing 94 when the valve member74 is in its open position and the plane sloped in a manner toefficiently direct liquid flow into the nozzle 99. In contrast, asillustrated in FIG. 10, the liquid-facing surface 97 of a valve shoulder86 found in a conventional beer dispensing faucet 98 is blunt andgenerally vertically planar. Furthermore, such a design results inliquid that is abruptly redirected as indicated by liquid flow lines 96.Such abrupt redirection of liquid can cause turbulence.

[0083] Since some of the liquid flowing through the valve chamber 79must pass the valve neck 85 on its way into the nozzle assembly 38, thecross section of the valve neck 85, illustrated in FIG. 9, isstreamlined for liquid flow in this direction.

[0084] Alternatively to the above described embodiment, which assumesmanual movement of the valve member 74, the energy required to move thevalve member 74 between its open and closed positions may be provided byan automatic or motor-operated means. For instance, in one embodiment, alinear actuator connected to the valve shoulder 86 may replace thefunction of the pushing and pulling of the handle lever 75 in moving thevalve member 74 from its closed position to its open position and back.Additionally, the valve member 74 may be moved via electromagneticmeans, in a manner similar to the solenoids used to control water flowin household appliances. Also, a geared or other rotary valve movementmechanism may also function to move the valve member 74 between itsclosed and open positions. Energy for rotating such gears may beprovided by electromechanical or manual means.

[0085] Preferably, liquid flowing through valve assembly 37 is directedimmediately into the nozzle assembly 38, as shown in FIG. 2. Preferably,nozzle assembly 38 comprises a downward-extending nozzle 99 and a liquiddispersion member or flow redirector 100 positioned near the lower end101 of nozzle 99. Liquid flowing past the valve assembly 37 into thenozzle assembly 38 will tend to accelerate due to the effects ofgravity. Nozzle assembly 38 fulfills four primary functions. First,viscous forces acting between the nozzle interior surface 102 and theliquid serve to slow the velocity of the liquid flow, somewhatcounteracting the acceleration of the liquid due to gravity. Second, thenozzle interior surface 102 is shaped so as to minimize the chance ofair moving up into the system when valve member 74 is in its openposition. A solid, air-free liquid stream serves to minimize foaming ofthe liquid within the nozzle assembly 38. Third, the flow redirector 100serves to redirect the flow of liquid exiting the nozzle assembly 38 ina manner that minimizes the turbulence and foaming caused when theliquid impacts the inside surface of the container being filled.Preferably, nozzle assembly 38 is long enough so that the flowredirector 100 is able to reach the bottom of the largest container tobe dispensed, allowing for the filling of containers at or near theirbottoms. In a preferred embodiment, nozzle assembly 38 is from about 3inches (7.62 cm) to about 15 inches (38.1 cm) in length. Morepreferably, nozzle assembly 38 is from about 4 inches (10.16 cm) toabout 12 inches (30.48 cm) in length. Still more preferably, nozzleassembly 38 is from about 8 inches (20.32 cm) to 10 inches (25.4 cm) inlength.

[0086] A liquid stream 103 flowing from a conventional faucet 98 isshown in FIG. 11. In the absence of a nozzle 99, the velocity of liquidexiting faucet 98 increases as the liquid falls due to gravity. Thisacceleration results in a decreasing cross sectional area of the liquidstream 103 as the liquid falls farther and farther away from the faucet98. The general shape of this profile is parabolic and its specificprofile depends on the flow rate of the liquid and the diameter of thefaucet outlet 104. Using Bernoulli's equation along with basic geometry,the cross sectional area of the liquid stream 103 at a given distancefrom the faucet outlet 104 can be calculated. According to Bernoulli'sequation:${p_{1} + {\frac{1}{2}\rho \quad V_{1}^{2}} + {\rho \quad {gz}_{1}}} = {p_{2} + {\frac{1}{2}\rho \quad V_{2}^{2}} + {\rho \quad {gz}_{2}}}$

[0087] where p₁, p₂ is the liquid pressure at the faucet outlet 104 andat some given distance from the faucet outlet 104, respectively

[0088] ρ is the density of the liquid

[0089] V₁, V₂ is the linear velocity of the liquid stream 103 at thefaucet outlet 104 and at some given distance from the faucet outlet 104,respectively

[0090] g is the acceleration due to gravity

[0091] z₁ and z₂ refer to points at the faucet outlet 104 and some givendistance from the faucet outlet 104, respectively

[0092] Since a free flowing liquid stream 103 is at atmosphericpressure, P₁=P₂=O. Setting z₁=0, Z₂=h and renaming V₂ as V₀ and V₁ asV_(h) provides as equation for V_(h) in terms of h, where V_(h) is thelinear velocity of the liquid stream 103 at a vertical distance, h,beneath the faucet outlet 104. $\begin{matrix}{{0 + {\frac{1}{2}\rho \quad V_{h}^{2}} + {\rho \quad g*0}} = {0 + {\frac{1}{2}\rho \quad V_{0}^{2}} + {\rho \quad {gh}}}} \\{{\frac{1}{2}\rho \quad V_{h}^{2}} = {{\frac{1}{2}\rho \quad V_{0}^{2}} + {\rho \quad {gh}}}} \\{V_{h}^{2} = {V_{0}^{2} + {2{gh}}}} \\{V_{h} = \sqrt{V_{0}^{2} + {2{gh}}}}\end{matrix}$

[0093] where V₀ is the linear velocity of the liquid stream 103 at thefaucet outlet 104.

[0094] The flow rate of a liquid stream 103 can be related to the liquidstream 103 linear velocity and the liquid stream 103 cross sectionalarea according to the following equation:

Q=A ₀ V ₀

[0095] where Q is the flow rate of the liquid

[0096] A₀ is the cross sectional area of the faucet outlet 104

[0097] V₀ is the linear velocity of the liquid stream 103 at the faucetoutlet 104.

[0098] Solving for V₀ and substituting in the equation for V_(h) yieldsthe following:$V_{h} = \sqrt{( \frac{Q}{A_{0}} )^{2} + {2{gh}}}$

[0099] For a circular faucet outlet 104, A₀ can be expressed in terms ofD₀, the diameter of the faucet outlet 104: $\begin{matrix}{A_{0} = {\pi ( \frac{D_{0}}{2} )}^{2}} \\{A_{0} = \frac{\pi \quad D_{0}^{2}}{4}}\end{matrix}$

[0100] One more substitution solves for V_(h) in terms of D₀:$\begin{matrix}{V_{h} = \sqrt{( \frac{Q}{\frac{\pi \quad D_{0}^{2}}{4}} )^{2} + {2{gh}}}} \\{V_{h} = \sqrt{( \frac{4Q}{\pi \quad D_{0}^{2}} )^{2} + {2{gh}}}} \\{V_{h} = \sqrt{\frac{16Q^{2}}{\pi^{2}\quad D_{0}^{4}} + {2{gh}}}}\end{matrix}$

[0101] Additionally, since the flow rate of the liquid is constantthroughout a compressionless system:

Q=A _(h) V _(h)

[0102] where Q is the volumetric flow rate of the liquid

[0103] A_(h) is the cross sectional area of the liquid stream 103 at adistance h from the faucet outlet 104

[0104] V_(h) is the linear velocity of the liquid stream 103 at adistance h from the faucet outlet 104

[0105] Solving the above for A_(h) and substituting in the previousdefinition of V_(h), the cross sectional area of the liquid stream 103,A_(h), can be determined as a function of its vertical distance h fromthe faucet outlet 104, the diameter of the faucet outlet 104 and theliquid flow rate: $\begin{matrix}{Q = {V_{h}A_{h}}} \\{A_{h} = \frac{Q}{V_{h}}} \\{A_{h} = \frac{Q}{\sqrt{\frac{16Q^{2}}{\pi^{2}\quad D_{0}^{4}} + {2{gh}}}}}\end{matrix}$

[0106] Preferably, the cross sectional area profile of the nozzleassembly 38 matches the cross sectional area profile of a free-fallingliquid stream 103, as calculated using the above equation. In thisembodiment, the cross sectional area of the nozzle 99 graduallydecreases from top to bottom. In a preferred embodiment, where a flowredirector is used, nozzle 99 widens near its distal end to accommodatethe flow redirector 100, but the cross sectional area of the resultingconcentric annulus preserves the continuity of this gradually decreasingcross sectional area to the point of the nozzle assembly outlet 105. Asshown, the concentric annulus maintains this gradually decreasing crosssectional area through the use of a flow director whose flow redirectorshaft 106 gradually increases in cross sectional area from top tobottom. Alternatively, the flow redirector 100 may have a flowredirector shaft 106 of constant diameter if the distal end of thenozzle 99 were to have a gradually decreasing cross section (not shown).A nozzle assembly 38 with a cross sectional area profile that matchesthe profile of a free falling liquid stream 103 serves to keep theliquid flowing through the nozzle assembly 38 in constant contact withthe nozzle interior surface 102. In this manner, viscous forces actingbetween the liquid and the nozzle interior surface 102 serve todecelerate the liquid. Additionally, air is unable to bubble up into thenozzle assembly 38 as long as the liquid is flowing at the flow rate forwhich the nozzle assembly 38 is optimized.

[0107] In an alternative embodiment of the nozzle assembly 38, shown inFIG. 12, a nozzle 107 with a linear taper approximates the graduallydecreasing cross sectional area of nozzle 99 with a cross-sectional areaprofile that matches that of a free-flowing liquid stream.

[0108] In another embodiment of the nozzle assembly 38, shown in FIG.13, a cylindrical nozzle 108 is used. In this embodiment, the crosssectional area of the cylindrical nozzle 108 is constant until the flowredirector 100 is introduced in which case the decrease incross-sectional area due to the positioning of the flow redirector 100is sufficient to prevent air from entering the cylindrical nozzle 108while liquid is flowing. Thus, the cross sectional area of the internalpassageway decreases from the liquid receiving end of the nozzle to theliquid dispensing end of the nozzle.

[0109] In still another embodiment, shown in FIG. 14, the nozzleassembly 38 contains two or more flow-straightening channels 109 thatserve to reduce any lateral movement of liquid in the nozzle assembly 38and decrease the turbulence of liquid flowing through the nozzleassembly 38. Preferably, nozzle 99 is subdivided into at least twochannels 109, and preferably three to ten channels 109. More preferably,nozzle 99 is divided into four equally sized channels 109. FIG. 15, FIG.16 and FIG. 17 illustrate, in cross-section, various embodiments of achanneled nozzle.

[0110] The Reynolds number provides an indication as to the laminar orturbulent nature of liquid flow. The Reynolds number for a nozzle 99 ofcircular cross-section without flow-straightening channels 109 can beexpressed as follows: ${Re} = \frac{\rho \quad {VD}}{\mu}$

[0111] The Reynolds number for a non-circular conduit can be determinedfrom the following equation:${Re}_{h} = \frac{\rho \quad {VD}_{h}}{\mu}$

[0112] where Re_(h) is the Reynolds number based on the hydraulicdiameter. The hydraulic diameter is defined as D_(h)=4A/P where A is thecross-sectional area of the conduit and P is the perimeter of theconduit. For each equally sized, semicircular, wedge-shaped channel 109in the nozzle assembly 38:$A = {{\frac{1}{n}\pi \quad ( \frac{D}{2} )^{2}} = {\frac{1}{n}{\pi ( \frac{D^{2}}{4} )}}}$${4A} = {{4( \frac{1}{n} )\pi \frac{D^{2}}{4}} = \frac{\pi \quad D^{2}}{n}}$$P = {{{2( {\frac{1}{2}D} )} + \frac{\pi \quad D}{n}} = {{D + \frac{\pi \quad D}{n}} = \frac{( {n + \pi} )D}{n}}}$$D_{h} = {\frac{4A}{P} = {\frac{\frac{\pi \quad D^{2}}{n}}{\frac{( {n + \pi} )D}{n}} = {( \frac{\pi}{\pi + n} )D}}}$${Re}_{h} = {\frac{\rho \quad {VD}_{h}}{\mu} = {( \frac{\pi}{\pi + n} )\frac{\rho \quad {VD}}{\mu}}}$

[0113] where D is the inside diameter of the nozzle 99 and n is thenumber of equally sized, semicircular, wedge-shaped channels 109.Comparing the Reynolds number of the nozzle 99 with the channels 109 tothe nozzle 99 not containing any flow-straightening channels yields thefollowing ratio:$\frac{{Re}_{h}}{Re} = {\frac{( \frac{\pi}{\pi + n} )\frac{\rho \quad {VD}}{\mu}}{\frac{\rho \quad {VD}}{\mu}} = \frac{\pi}{\pi + n}}$

[0114] Thus, the Reynolds number of liquid flowing through the nozzleassembly 38 with the flow-straightening channels 109 has been reduced bya factor of (π)/(π+n) as compared to a nozzle assembly 38 withoutflow-straightening channels in place. As indicated, increasing thenumber of channels 109 would further decrease the Reynolds number of theliquid flowing through the nozzle 99. Additionally, the surfaces 110 ofeach flow-straightening channel 109 increase the available surface areaupon which viscous forces acting between the liquid and the surfaces 110can form, thereby further decelerating the liquid as it travels throughthe nozzle 99.

[0115] The nozzle assembly 38 may be insulated and/or cooled by liquidor other means known in the art, including, but not limited to foam,air, circulated glycol, circulated water and thermoelectric means. Sincethe nozzle assembly 38 is exposed to the ambient air, it may warm to theambient temperature in the absence of such insulation or coolingmechanism. Extending the glycol lines of a glycol-cooled dispensingsystem such that they coil within the nozzle assembly 38 (not shown) maybe used to keep the nozzle assembly 38 cold.

[0116] A principal cause of excessive foaming when dispensing beer ishaving the beverage hit the bottom of the container at a great velocityor in an otherwise turbulent manner. Flow redirector 100 minimizesfoaming by gently redirecting and dispersing liquid exiting the nozzleassembly 38 in a manner that reduces the force of impact between theliquid and the container. As shown by simulated liquid flow lines 96 inFIG. 18, liquid traveling through the nozzle assembly 38 is evenlydispersed around the flow redirector shaft 106. As liquid flows past theflow redirector 100, it is gently redirected from flowing in a generallydownward direction into flowing in a radial direction. Preferably,liquid exiting the nozzle assembly 38 is dispersed radially, in an even360-degree pattern that also possesses a downward vector. Such a patternhas been determined to minimize foaming of the beverage as it isdispensed for a wide variety of container sizes. A lip 111 at the lowerend of nozzle 99 may also be present. Lip 111 is preferably rounded,although other shapes are contemplated, so as to improve the flowcharacteristics of liquid exiting the nozzle assembly outlet 105.

[0117] Preferably, flow redirector 100 is a streamlined object. In apreferred embodiment, the proximal end 112 of flow redirector 100 is inthe shape of an elliptical dome. In this embodiment, a round flowredirector shaft 106 gradually widens towards the flow redirector base113 so as to redirect the liquid flow with the least amount ofturbulence. Preferably, the horizontal cross-section along the entirelongitudinal length of the flow redirector 100 is circular, althoughother shapes, as long they do not substantially interfere with the flowof the liquid, are contemplated. The flow redirector base 113 is alsopreferably circular and flat such that the bottom of a flat-bottomedcontainer can be positioned flush against the flow redirector base 113.However, the bottom of flow redirector base 113 may also have a somewhatconcave surface as long as the peripheral edge of the bottom of the flowredirector base 113 substantially contacts the bottom of the containerto be filled. The exterior surface of the flow redirector 100 ispreferably smooth.

[0118] While a tall, wide flow redirector 100 would serve to decreasethe turbulence caused when redirecting the liquid, such a flowredirector 100 would result in a long, wide nozzle assembly 38 thatwould have difficulty fitting into smaller containers. For this reason,a more compact flow redirector 100 is desirable. Preferably, the flowredirector 100 is between 0.5 inches (1.27 cm) and 8 inches (20.32 cm)when measured between its proximal end 112 and its base 113. Morepreferably, the flow redirector 100 is between 1 inch (2.54 cm) and 4inches (10.16 cm) when measured along this length. Still morepreferably, the flow redirector 100 is 2 inches (5.08 cm) when measuredalong this length. Preferably, the flow redirector base 113 measuresbetween 0.25 inches (0.635 cm) and 5 inches (12.7 cm) at its widestpoint. More preferably, the flow redirector base 113 measures between0.5 inches (1.27 cm) and 2 inches (5.08 cm) at its widest point.Additional embodiments of flow redirector 100 are illustrated in FIG.20, FIG. 21, and FIG. 22. Many other flow redirector 100 shapes andconfigurations are possible that accomplish the task of reducing theamount of foaming caused when the liquid leaves the nozzle assembly 38and impacts a container. Preferably, the flow redirector is obconical.

[0119] Preferably, flow redirector 100 is generally not movable, but isremovable. Flow redirector 100 may be attached to the inside of thenozzle 99 via one or more support structures 114. Support structures 114are of sufficient strength to hold the flow redirector 100 centeredalong the axis of the nozzle 99, even in the presence of a liquidstream. To minimize their disturbance to liquid flow, support structures114 are preferably streamlined and comprise a rounded proximal end 115that gradually tapers to a point at the distal end 116. An airfoilshape, as shown in FIG. 19, has been found to minimize the turbulencecaused by the support structures 114. In the case of a nozzle assembly38 that contains flow-straightening channels 109, flow redirector 100may not require support structures 114 to hold it in place as it may beaffixed directly to the surfaces 110 forming the flow-straighteningchannels 109.

[0120] Flow redirector 100 is positioned longitudinally within thenozzle assembly 38 such that a nozzle assembly outlet 105 is formedbetween the lip 111 of the nozzle assembly 38 and the flow redirector100 that allows liquid to leave the nozzle assembly 38 and enter thecontainer. The size of the nozzle assembly outlet 105 must be largeenough to allow liquid to rapidly exit the nozzle assembly 38, and smallenough to obtain an even, radial dispersion of liquid into thecontainer. The optimal size of the nozzle assembly outlet 105 varieswith liquid flow rate, nozzle 99 diameter and the particular shape ofthe flow redirector 100. Preferably, the height of the nozzle assemblyoutlet 105 as measured as the vertical distance between the lip 111 ofthe nozzle 99 and flow redirector 100 is between 0.2 inches (0.508 cm)and 1.5 inches (3.81 cm). More preferably, the height of the nozzleassembly outlet 105 is between 0.35 inches (0.889 cm) and 0.6 inches(1.524 cm). Still more preferably, the height of the nozzle assemblyoutlet 105 is between 0.4 inches (1.016 cm) and 0.5 inches (1.27 cm).

[0121] While the height of the nozzle assembly outlet 105 may be a fixeddistance, another embodiment of this invention, shown in FIG. 23 andFIG. 24, allows for fine-tuning of the specific longitudinal position ofthe flow redirector 100 within the nozzle assembly 38 via set screws 117and countersunk slots 118 in the nozzle 99 allowing for longitudinalmovement of the flow redirector 100 upon loosening the set screws 117.In moving the flow redirector 100 longitudinally along the axis of thenozzle assembly 38, the height of the nozzle assembly outlet 105 ischanged. The set screws 117 may also be completely removed from thenozzle assembly 38 such that the flow redirector 100 can be removed fromthe nozzle assembly 38 for cleaning or maintenance purposes.

[0122] In another embodiment of this invention, a diffuser 121 is placedupstream from the valve assembly 37 so as to increase the crosssectional area of liquid entering the valve assembly 37 in a manner thatminimizes the amount of turbulence. Preferably, the diffuser 121 tapersfrom its throat end 119 to its exit end 120. In one embodiment, shown inFIG. 25, a conical diffuser 121 is positioned within the neck assembly36 of the rapid beverage dispensing device 35. The axis of the conicaldiffuser 121 in this embodiment is aligned vertically within the neckassembly 36 of the rapid beverage dispense device 35, although it mayalso posses a radius of curvature. Preferably the divergence angle ofthe conical diffuser 121, as measured as the angle between thelongitudinal axis of the conical diffuser 121 and the conical diffuserwall 122, is relatively small. A large divergence angle typicallyresults in increased turbulence as the liquid is forced to expand incross-sectional area over a short distance. To facilitate diffusionwhile minimizing turbulence, preferably the conical diffuser 121possesses a divergence angle of fewer than 25 degrees. More preferably,the divergence angle is fewer than 12 degrees, and even more preferablyis 8 or fewer degrees.

[0123] Under certain conditions, it may be desirable to slow the flowrate of the liquid leaving the rapid beverage dispensing device 35. Inanother embodiment of the present invention, shown in FIG. 26, apressure-reducing element 123 is introduced into this system inconjunction with a multi-way valve 124 in order to optionally slow theflow rate of the liquid being dispensed. While a pressure-reducingelement 123 can take many forms, preferably, the pressure-reducingelement 123 consists of a length of narrow diameter tubing. Thepressure-reducing element 123 is coiled within the neck assembly 36 ofthe rapid beverage dispensing device 35 so as to minimize its spacerequirements.

[0124] The inbound end 125 and outbound end 126 of the pressure-reducingelement 123 are connected to a multi-way valve 124 positioned at theneck base 127 of the rapid beverage dispensing device 35. As shown inone embodiment in FIG. 27, in one position, the multi-way valve 124provides an unimpeded, full-port opening between the rapid beveragedispensing device 35 and the rest of the beer dispensing system 39.Liquid flow arrows 128 indicate the path of liquid flow through themulti-way valve 124. In this position, the liquid flow completely bypasses the pressure-reducing element 123 and liquid is dispensed fromthe rapid beverage dispensing device 35 at its normal flow rate as ifthe pressure-reducing element 123 were not present.

[0125] As shown in FIG. 28, in its other position, the multi-way valve124 directs liquid through the pressure-reducing element 123 on its waythrough the rapid beverage dispensing device 35. In this position,liquid entering the multi-way valve 124 is directed to the outboundvalve port 129 which is attached to the inbound end 125 of thepressure-reducing element 123. Energy from the beer dispensing system 39continues to move the liquid through the entire length of thepressure-reducing element 123 before the liquid re-enters the multi-wayvalve 124 through its inbound valve port 130 which directs the liquidfrom the outbound end 126 of the pressure-reducing element 123 throughthe rapid beverage dispensing device 35. Because the liquid re-enteringthe multi-way valve 124 has experienced a drop in pressure, the liquidre-enters the rapid beverage dispensing device 35 at a reduced flowrate, preferably the optimal flow rate of a conventional beer dispensingfaucet.

[0126] It is therefore intended that the foregoing detailed descriptionbe regarded as illustrative rather than limiting, and that it beunderstood that it is the following claims, including all equivalents,that are intended to define the spirit and scope of the invention.

1. A beverage dispensing apparatus for dispensing a pressurized beveragecomprising a nozzle through which the pressurized beverage at leastinitially exits to atmospheric conditions having an internal passageway,a liquid receiving end adapted to attach as the end element of apressurized beverage dispensing system, and a liquid dispensing end thatdispenses the pressurized beverage at least initially to atmosphericconditions, wherein the cross-sectional area of the internal passagewayof the nozzle decreases from the liquid receiving end to the liquiddispensing end.
 2. The beverage dispensing apparatus of claim 1 whereinthe decrease in cross-sectional area of the internal passageway iscontinuous.
 3. The beverage dispensing apparatus of claim 2 wherein thecross sectional area profile of the internal passageway approximates thecross sectional area profile of a free falling stream of liquid atambient pressure.
 4. The beverage dispensing apparatus of claim 2wherein the length of the nozzle is at least about three inches.
 5. Thebeverage dispensing apparatus of claim 4 wherein liquid flowing throughthe nozzle is in substantially constant contact with the surface of theinternal passageway.
 6. The beverage dispensing apparatus of claim 1comprising a liquid dispersion member having a liquid receiving end anda liquid dispersing end, the liquid dispersing end extending from theliquid dispensing end of the nozzle and radially dispersing the beverageexiting the liquid dispensing end of the nozzle.
 7. The beveragedispensing apparatus of claim 6 wherein the liquid dispersion member isremovably supported within the liquid dispensing end of the internalpassageway of the nozzle.
 8. The beverage dispensing apparatus of claim6 wherein the liquid dispersion member further comprises a stem ofsubstantially uniform circumference and a substantially obconical liquiddispersing surface.
 9. The beverage dispensing apparatus of claim 8wherein the liquid dispersing surface of the liquid dispersion memberextends from the liquid dispensing end of the nozzle from about 0.2inches to about 1.5 inches.
 10. The beverage dispensing apparatus ofclaim 9 wherein the liquid dispersing surface of the liquid dispersionmember extends from the liquid dispensing end of the nozzle from about0.35 inches to about 0.6 inches.
 11. The beverage dispensing apparatusof claim 10 wherein the liquid dispersing surface of the liquiddispersion member extends from the liquid dispensing end of the nozzlefrom about 0.4 inches to about 0.5 inches.
 12. The beverage dispensingapparatus of claim 6 wherein the distance that the liquid dispersingsurface of the liquid dispersion member extends from the liquiddispensing end of the nozzle is adjustable.
 13. The liquid dispersionmember of claim 8 wherein the liquid dispersing surface has a graduallydecreasing slope.
 14. The liquid dispersion member of claim 13 whereinthe liquid dispersing surface disperses liquid from the nozzle at anangle to the longitudinal axis of the nozzle.
 15. The liquid dispersionmember of claim 14 wherein the dispersing surface disperses liquid fromthe nozzle substantially perpendicular to the axis of the liquiddispersion member.
 16. The beverage dispensing apparatus of claim 1wherein the cross-sectional area profile of the internal passagewaygradually decreases from top to bottom according to the followingformula:$A_{h} = \frac{Q}{\sqrt{\frac{16Q^{2}}{\pi^{2}\quad D_{0}^{4}} + {2{gh}}}}$


17. The beverage dispensing apparatus of claim 1 wherein the internalpassageway of the nozzle comprises at least two vertical channels. 18.The beverage dispensing apparatus of claim 17 wherein the internalpassageway of the nozzle comprises four vertical channels.
 19. Abeverage dispensing system comprising: a container holding a carbonatedbeverage; an energy source that pressurizes the carbonated beverage inthe container; a valve in fluid communication with the beverage in thecontainer, the valve having an open position and a closed position; anozzle having a liquid receiving end in fluid communication with thevalve, an internal passageway having a cross sectional area throughwhich said carbonated beverage flows when said valve is in the openposition, and a liquid dispensing end having an opening through whichthe carbonated beverage at least initially exits to atmosphericconditions, wherein the cross-sectional area of the internal passagewayof the nozzle decreases from the liquid receiving end to the liquiddispensing end such that the carbonated beverage flowing through thenozzle is in substantially constant contact with the surface of theinternal passageway from the liquid receiving end to the liquiddispensing end.
 20. The beverage dispensing system of claim 19 whereinthe decrease in the cross-sectional area of the internal passageway ofthe nozzle is continuous.
 21. The beverage dispensing system of claim 20wherein the cross sectional area profile of the internal passagewayapproximates the cross sectional area profile of a free falling streamof liquid at ambient pressure.
 22. The nozzle of claim 19 comprising aliquid dispersion member having a liquid receiving end and a liquiddispensing end.
 23. The beverage dispensing system of claim 22 whereinthe liquid dispersion member is removably supported within the liquiddispensing region of the internal passageway of the nozzle.
 24. Thebeverage dispensing system of claim 23 wherein the liquid dispersionmember is substantially immobile.
 25. The beverage dispensing system ofclaim 22 wherein the liquid dispersion member further comprises asubstantially obconical liquid dispersing surface.
 26. The beveragedispensing system of claim 25 wherein the liquid dispersing surface ofthe liquid dispersion member extends from the liquid dispensing openingof the nozzle.
 27. The beverage dispensing system of claim 26 whereinthe liquid dispersing surface of the liquid dispersion member extendsfrom the liquid dispensing end of the nozzle from about 0.2 inches toabout 1.5 inches.
 28. The beverage dispensing a system of claim 24wherein the liquid dispersion member is adjustable.
 29. The liquiddispersion member of claim 25 wherein the liquid dispersing surface hasa gradually decreasing slope.
 30. The liquid dispersion member of claim29 wherein the liquid dispersing surface disperses liquid from thenozzle at an angle to the longitudinal axis of the nozzle.
 31. Theliquid dispersion member of claim 30 wherein the liquid dispersingsurface disperses liquid from the nozzle substantially perpendicular tothe axis of the nozzle.
 32. The liquid dispersion member of claim 30wherein the dispersing surface disperses liquid from the radially fromthe liquid dispersion member.
 33. The beverage dispensing system ofclaim 19 wherein the nozzle further comprises at least two verticalchannels.
 34. The beverage dispensing system of claim 33 wherein thevalve comprises a valve head, a valve stem and a valve body.
 35. Thevalve of claim 34 wherein the valve body further comprises a valveshoulder that is on a bias to the valve stem.
 36. The valve of claim 35wherein the surface of the valve shoulder conforms to the inner contourof the valve housing.
 37. The valve of claim 36 wherein a portion of thesurface of the valve shoulder forms an acute angle to the axis of thevalve stem.
 38. The valve of claim 37 wherein the surface of the valveshoulder is concave.
 39. A beverage dispensing apparatus comprising: anozzle; a valve assembly; liquid dispersion member; and a diffuserupstream of the valve assembly, the diffuser having a first end, asecond end, and an internal passageway between the first end and thesecond end; wherein the cross sectional area of the internal passagewayof the diffuser increases from the first end to the second end.
 40. Thebeverage dispensing apparatus of claim 39 wherein the angle ofdivergence from the axis of the diffuser to the surface of the internalpassageway is less than 25 degrees.
 41. The beverage dispensingapparatus of claim 40 where in the divergence angle is 12 degrees orless.
 42. The beverage dispensing apparatus of claim 41 wherein thedivergence angle is 8 degrees or less.
 43. A beverage dispensingapparatus comprising: means for introducing the beverage to be dispensedinto the beverage dispensing apparatus; means for increasing the flowrate of liquid through the apparatus; means for decreasing turbulence inthe flow of the liquid; means for reducing foaming of liquid dispensedfrom the apparatus; and means for the controlled dispensing of liquidfrom the apparatus.
 44. The beverage dispensing apparatus of claim 43further comprising means for reducing pressure.
 45. The beveragedispensing apparatus of claim 44 further comprising means for coolingliquid in the beverage dispensing apparatus.
 46. The beverage dispensingapparatus of claim 45 further comprising means for selectivelycontrolling the fluid flow rate through the beverage dispensingapparatus.
 47. A beverage dispensing apparatus comprising: a containerholding a carbonated beverage; an energy source that pressurizes thecarbonated beverage in the container; a valve in fluid communicationwith the beverage in the container, the valve having an open positionand a closed position, the valve having a valve housing, a valve seatand a valve head, the valve housing having an inlet and an outlet and acurved interior surface defining a curved fluid chamber, and a valveshoulder having a liquid facing surface, wherein the liquid facingsurface is contoured to match the curvature of the interior surface forthe valve housing.
 48. The beverage dispensing apparatus of claim 47wherein the liquid facing surface is generally the shape of a portion ofan arced cylinder.
 49. The beverage dispensing apparatus of claim 48wherein the liquid facing surface is generally concave and has two radiiof curvature.
 50. The beverage dispensing apparatus of claim 47 whereinthe valve head is generally elliptical.
 51. The beverage dispensingapparatus of claim 47 wherein the valve head is generally spherical. 52.The beverage dispensing apparatus of claim 47 wherein the valve headopens in the direction of the valve housing inlet.
 53. The beveragedispensing apparatus of claim 1 comprising means for selectivelyreducing the pressure of the liquid upstream from the nozzle.
 54. Thebeverage dispensing apparatus of claim 53 wherein the means forselectively reducing the pressure of the liquid upstream from the nozzlecomprises a multi-way valve.
 55. The beverage dispensing apparatus ofclaim 54 wherein the means for selectively reducing the pressure of theliquid upstream from the nozzle comprises a length of beverage tubing.56. The beverage dispensing apparatus of claim 53 wherein the means forselectively reducing the pressure of the liquid upstream from the nozzlecomprises a multi-way valve and a length of beverage tubing, wherein themulti-way valve is capable of selectively routing fluid flow through oraround the length of tubing.
 57. A method for decreasing the formationof foam in carbonated beverages comprising: directing the flow of liquidto a liquid dispensing nozzle having a liquid flow control valve havingan open position and a closed position, a liquid receiving opening, aliquid dispensing opening, and a liquid flow path of decreasingcross-section; positioning the bottom of the inside of a liquidreceiving receptacle near the opening of the nozzle; moving the valve tothe open position to permit the flow of the liquid through the nozzle;directing the flow of liquid through the nozzle to the fluid dispensingopening in a path generally parallel to the nozzle; and redirecting theflow of liquid by means of a liquid flow redirector at the opening ofthe nozzle in a direction generally tangential to the liquid receivingreceptacle.